Governor for prime mover with compressed air control for adjusting it to a wide range of speeds



R. R. CROOKSTON Oct. 20, 1953 GOVERNOR FOR PRIME MOVER WITH COMPRESSED AIR CONTROL FOR ADJUSTING IT TO A WIDE RANGE OF SPEEDS Filed Nov. 15, 1950 3 Sheets-Sheet l FIG. IA

ENGINE SHAFT AND GEAR IN VENTOR! Roberf R. Crooksfon, 7 BY M) 9 I I I 9 I ATTORNEY.

W 2. Aim? Oct. 20, 1953 Filed Nov. 13, 1950 R. R. CROOKSTON GOVERNOR FOR PRIME MOVER WITH COMPRESSED AIR CONTROL FOR ADJUSTING IT TO A WIDE RANGE OF SPEEDS 5 Sheets-Sheet 2 so I 6! I I 46 44 5o 5: I I13 I I 115 i I m n4 M. w l :12 i 7 10s I"; .100 n I04 I3 I M FIG. 3.

INVENTOR;

Robert R. Crooks 'fon,

ATTORNEY.

1953 I R. R. CROOKSTON GOVERNOR FOR PRIME MOVER WITH COMPRESSED AIR CONTROL FOR ADJUSTING IT TO A WIDE RANGE OF SPEEDS Filed Nov. 15, 1950 5 Sheets-Sheet 3 INVENTOR. Robert R. Crooksfon,

ATTORNEY.

Patented Oct. 20, 1953 GOVERNOR FOR PRIME MOVER WITH COM:-

PRESSED AIR. CONTROL FOB ADJUSTING IT; TO A WIDE RANGE OF SPEEDS Robert R. Crookston, Houston, Tex, assignor, by

mesne assignments, to Standard Oil Development Company, Elizabeth, N. J., a. corporationof Delaware Application November 13, 1950, Serial No. 195,175,

11 Claims.

This invention relates to a governing mechar nism designed to maintain the speed of a prime mover with which it is associated within reasonably constant limits irrespective of the load which may be, placed on the prime mover.

In many of the instances in which rotating engines are utilized, it is desirable to have a readily controllable, variable speed governor effective over a. wide range of engine speeds. For example, in ship propulsion, means employed in connection with the ships engines for accomplishing the aforementioned purpose is often employed. Another example is encountered in well drilling. In well drilling it is often desirable to. operate, the prime mover employed at a relatiyely constant, but adjustably variable, speed. There, are, of course, many other instances n which it is desirable. to. operate a rotating engine, at relatively constant speed. irrespective of the, load placed thereon, and it, is further desirable. that the means employed for controlling the speed be adjustable to any speed at which it is, desired that the engine. be. operated. It is, of course, essential that such means be stable at the operating speed maintained.

The, rotative speed of prime movers is commonly controlled by means. of governors. While various difierent typesv of governors have been developed, the present invention is concerned with a centrifugal governor. Centrifugal, governors depend for their action upon centrifugal force. and consist essentially of a pair of masses retating about. a spindle driven by the prime mover, the. speed of which. is tov be controlled. These masses, when rotated, te d telly outwardly, the governor being provided with a controlling iorcefto resist this outward motion. With an increase in speed, the controlling forceis overcome and the masses. move outwardly, this outward r'notionproducing linear motion in the spindle.

The spindle, in turn, is. mechanically connected to. valves. supplying the prime mover with work.-

ing. fluid or fuel, reducing or increasing the; sup.-

.ply of working fuel, thereto depending upon whether the speed of the prime mover is greater than or less than the desired speed.

In the past, a number of different types of centrifugal governors have been developed. One Well-known type is that invented by James Watt. In the Watt governor, also known as the conical pendulum governor, the revolving masses are balls attached to a vertical spindle by link arms and the controlling force consists of the weight of the balls themselves In this mechanism the centrifugal force exerted by the rotating balls is combatted by the weight of these balls.

Another well-known governor, commonly known as the Porter governor, consists of the Watt governor with the addition of a heavy; movable weight surroundingthe vertical spindle. In the Porter governor, the centr fugal force exerted by the revolving balls is combatted by the force of gravity exerted on the heavy, movable Weight surrounding the spindle.

Unfortunately, neither the Watt governor nor the Porter governor is suitable for controlling the speed of a prime mover over a wide range of engine speeds. The Watt governor is not adjustable for different speeds, and while it is quite stable at relatively low speeds, it is unstable at intermediate and high speeds. On the other hand, the Porter governor can be so constructed as to be stable at medium and high speeds but then it is normally unstable at low speeds. 'Because of these inherent limitations in the Watt and Porter governors, another type of centrifugal governor, namely the spring-loaded type, has been developed.

The controlling force, in the spring-loaded governor, is wholly or partly produced by means of springs. In this type, the centrifugal force exerted by the rotating balls is combatted' by the force supplied either by a single spring or by a plurality of springs which may be arranged either in tension or in compression. If a single spring is used with the initial compression or tension of the spring preset to give different operating ranges, little difficulty will be experienced in providing a spring-loaded governor capable of adjustment for control over a 211 speed range. Inasmuch as the initial stress required is proportional to the square of the speed range covered, an initial stress in the. spring of 4:1 is required to take care of a 2:1 speed range. When, however, an attempt is made to provide a 10:1 speed range, the spring requirements are for a initial stress. Due to the finite characteristics of springs, the provision of a 100:1 initial stress is impractical.

Because it is impractical to employ a single spring only when it is desired to cover a Wide speed range, governors have been made available which employ two or more springs. If two or more springs with different rates are used operating in tandem, that is, first one is stressed and then the others are each stressed in turn by movement of the fly balls, the mean speed of governing may be, varied within limits, these limitations changing in the same number of discrete steps as there are springs in tandem. These multi-spring gevernprs may take two neral f rm.- n one term the, fly b ls. n

arms are allowed to assume the same configuration at each chosen mean speed with the choice of the spring in use at any time and the initial loading on that spring being made by a screwdown device, or its equivalent, controlled either locally or remotely. In the other form the fly balls and arms are allowed to assume different configurations at each chosen mean speed; here the force from a second spring is realized after a chosen speed is reached with the initial loading of the springs adjustable within limits. The characteristics of either of these two type are such that, although the governor may be quite stable either when the prime mover is rotating at a low speed or when operating under full load, it is not both stable and reasonably sensitive throughout its speed range. It is even possible to select the springs so that the governor is both stable and reasonably sensitive at lou speeds and at high speeds but unstable in the intermediate speeds. Instability at intermediate speeds is particularly undesirable in that the governor hunts over a very wide range when any attempt is made to control the speed of the prime mover at an intermediate speed.

It is an object of the present invention to provide a governor for maintaining the speed of prime movers within reasonably constant limits, the governor being adjustable for controlling over a wide range of speeds. It is a further object of the present invention to provide a governor upon which the aforementioned adjustments can be accomplished without stopping the rotation of the prime mover or without disengaging the governor.

The present invention is fully described hereinafter in conjunction with the drawing in which Fig. 1 is a front view, partly in cross section, of the governing device of the present invention;

Fig. 1-A is the upper portion of the device shown in Fig. 1;

Fig. 2 is a view in elevation of one side of the device shown in Fig. 1;

Fig. 3 is a view in elevation of the other side of the device shown in Fig. 1;

Fig. 4 is a detailed view, partly in cross sec tion, of the piston and dash pot arrangement shown in the upper part of Figs. 1 and 1-A;

Fig. 5 is a fragmentary sectional view taken along the line VV of Fig. 4;

Fig. 6 is a perspective view showing the linkage between the yoke, the fuel rack, and the throttle arm shown in Fig. 1;

Fig. '7 is a view, partly in cross section, of

a modification of the piston and dash pot arrangement shown in Fig. 4; and

Fig. 8 is a view, partly in cross section, of a modification of a portion of the device shown in Figs. 1 to 6, inclusive.

In the drawing, like numerals refer to like parts throughout. Referring to Figs. 1 to 6, inclusive, and particularly to Fig. 1, I8 designates the governor housing. Rotatably supported within governor housing I II by means of bearings II and I2 is spindle I3. A bevel gear I4 is afiixed to the lower end of spindle l3 exteriorly of housing III. A governor weight supporting member I5 is afiixed to spindle I3 Within housing I0. L-shaped arm I6 carries governor weight I! at the end of one branch and a rotatably mounted wheel I8 pivoted to the end of the other branch by pin I9 is pivotally mounted on member I5 by means of a pin 20. L-shaped member I6 carrying governor weight IT at the end of one branch and a rota a w mounted wheel I8 pivoted to the end of the other branch by means of pin 99 is pivotally mounted on member I5 by means of pin 20. L-shaped members I6 and I6 are mounted on member I5 diammetrically opposite from each other, the longitudinal axis of pins 20 and 23 about which members I6 and It pivot being parallel to each other. L-shaped member It defines a projection 2i which is adapted to abut against surface 22 of member I5 when the L- shaped member IE is moved arcuately about pin 20 in a clockwise direction and defines a projection 23 which is designed to abut against surface 24 when L-shaped member I5 is moved arcuately about pin 26 in a counter-clockwise direction. L-shaped member I6 defines a projection ZI' which is designed to abut against surface 22 of member I5 when it is moved arcuately about pin 23' in a counter-clockwise direction and defines projection 23' which is designed to abut against surface 24 of member I5 when it is moved arcuately about pin 20' in a clock wise direction.

A collar 25 is mounted on the upper end 26 of spindle I3, which may be splined as shown, for longitudinal movement on said end. A yoke member 27 is mounted within housing In so that its central axis is coincident with the central longitudinal axis of spindle I3, yoke member 21 being supported above collar 25 by means of bearing 28. The outer surface 29 adjacent the upper end of yoke 21 moves slidably in contact with inner surface III of housing III. The outer surface of yoke member 21 intermediate its upper and lower ends define a pair of diametrically opposed slots 30 and 38, the purpose of which will be later described. The longitudinal axis of slots 30 and 3B is perpendicular to the longitudinal axis of yoke member 21. Yoke member 2! defines inwardly extending shoulder 3| at its lower end and upwardly extending shoulder 32 adjacent its upper end.

Concentrically arranged within yoke member 21 is stem 33. Slidably mounted on the lower end of stem 33 for longitudinal movement with respect thereto is spring-retaining member 34 which defines upwardly extending shoulder 35 and downwardly extending rim portion 36. The lower surface 31 of downwardly extending rim portion 36 abuts on shoulder 3| of yoke member 21. The height of rim portion 36 is such that contact between lower surface 38 of stem 33 and upper surface 39 of spindle I3 is prevented when yoke member 21 is moved to its upper limit of travel. Spring-retaining member 44 is threadedly engaged with the upper threaded end All of stem 33, spring-retaining member 40 defining downwardly projecting shoulder 42. In order to prevent the rotation'of upper spring-retaining member 40 on threaded end 4| of stem 33, a jam nut 43 is also threadedly engaged with threaded end portion 4| into position against spring-retaining member 40. Also threadedly engaged with the upper threaded end 4| of stem 33 above spring-retaining member 43 and jam nut 43 is a sleeve member 44. The height of sleeve 44 is such that its upper end 45 extends above the upper extremity of stem 33 and, accordingly, plug 46 is screw-threadedly engaged in said upper end. Plug 45 defines a conical-shaped tip 47 which projects above the upper end 45 of sleeve 44. Sleeve 44 moves freely through opening 48 defined by cap 49 of housing ID.

A spring-retaining member 52 is located in the upper section of governor body It and moves smaller diameter than shaft Ito is eccentrioally journalled in shaft I bridging the cut-away portion thereof, end I of shaft I04 extending beyond end I02 of shaft lei! and having bracket IOIl affixed thereto. Arms I0! and E68 are each afiixed at one end to shaft Ills, and pivotally connected to their other end are keys I09 and H0, respectively, which slide horizontally in slots 3i) and 30' of yoke member 2?. Bracket I06 is pivotally connected to one end of link I I l by means of pivot pin H2 and the other end of link Iii is pivotally connected to pointer H3 by means of pivot pin II 6. Pointer H3 is afiixed to shaft H5 which is supported for arcuate movement about its longitudinal axis by housing IIE. Shaft H5 actuates the mechanism which increases and decreases the amount of fuel admitted to the engine, the speed of which is being controlled by the governor of the present invention.

The operation of the embodiment shown in Figs. 1. to 6, inclusive, will now be described, the parts shown therein and their relation to each other having been fully described hereinbefore. In Figs. 1 and l-A, governor weights I? and II are shown in the position which they assume when spindle I3 is being rotated; that is, projections 23 and 23' of L-shaped members I6 and I6, respectively, abut on upper surface 2-1. of the governor weight supporting member I5. Yoke 2'! and collar 25 are in the full down position, spring 51 exerting a downward bias on yoke 21. Lower spring-retaining member 35 and stem 33 are also in the full down position, spring 5 5 biasing lower spring-retaining member 3 away from upper spring-retaining member 40. It will be further noted that pistons 65 and 58 are each in their full down position. When piston 65 is in its full down position and spindle I3 is not being rotated, conical tip 47 of plug t6 does not contact the recess 12 in the lower surface of the piston E8. The purpose for providing this space between tip 4! and recess '32 will become apparent from the description hereinafter given. Pistons G6 and 53 are forced in their full down position by admitting air to chamber 52 through channel as, the air being under suficien-t pressure to overcome the opposing bias exerted by spring I8.

Now suppose knob I03 is moved along bracket :03 to an idling position and further suppose that the engine which the governor is controlling is idling at a slow speed. This in turn means that spindle I3 will be rotated at a low speed and weights 5'! and II tend to move arcua-tely about pins and 26, respectively, in the direction indicated by the solid arrow. Since wheels I 8 and I8 carried by L-shaped members It and IS, respectively, abut against collar 25, outward movement of governor weights I! and I7 cause collar to be moved upwardly on spindle I3 in. sliding contact with the upper end 2B thereof. Upward motion of collar 25 causes upward motion of yoke 2'! against the bias of spring 5'1. Since lower spring-retaining member 34 abuts on shoulder 3I defined by yoke 27 and since spring 54 biases lower spring retaining member 35 away from upper spring-retaining member 40, stem 33 is carried upwardly by yoke 27 without compressing spring -54. This upward motion of yoke 2! is transferred through arms l0? and IE8 to shaft I04, thence through bracket I06, link III and pointer I I3 to shaft I I5 which is caused to be moved arcuately in such direction as to decrease the supply of fuel to the engine to be controlled and, therefore, to reduce its speed to that determined by the setting of knob I03"'along bracket I03.

Now with the engine idling at the slowed speed hereinbefore mentioned, assume that knob I03 is moved along bracket I03 to a position between the idling position and full throttle position. Movement of knob I03 in this direction produces corresponding arcuate movement of shaft I00, the arcuate movement of shaft I00 being transmitted through shaft I04 to bracket I06 and through link I! I and pointer H3 to shaft M5 to cause arcuate movement of shaft H5 in such a direction as to admit a larger quantity of fuel to the controlled engine. Admission of more fuel to the controlled engine causes the speed of this engine to increase and, accordingly, of spindle I3 to increase. This causes governor weights I! and IT to move even further away from the axis of spindle I3, thus raising yoke 27. Upward movement of yoke 27 further compresses low speed spring 51 and further raises stem 33 until conical tip 4%! of plug 46 moves into recess I2 and abuts against piston 65. When plug as contacts piston 66, further upward movement of stem 33- is opposed by the downward force exerted by said piston. This downward force may be termed the air cylinder net force which is the difference between the downward force exerted by piston 55 due to the air pressure applied thereto and the upward bias exerted by spring 18 on'said piston. If the air cylinder net force is less than the preloading of spring 54, further outward movement of governor weights l1 and I? move piston 65 upwardly until a balanced force point is reached, 1. e., until piston 66 opposes further upward movement of stem 33 without spring 54 being compressed. If, however, the air cylinder net force is greater than the preloading of spring 5 5, spring 54 will be compressed until its force equals the air cylinder net force.

It will be apparent that knob I03 may be moved along bracket I03 to the full throttle position or to any other position depending upon the speed at which it is desired that the controlled engine operate. If for any reason the speed of the controlled engine increases above the desired speed, governor weights I1 and II will move outwardly in the direction indicated by the solid arrow causing yoke 21 to move upwardly, thus reducing the supply of fuel to the controlled engine. If for any reason the speed of the controlled engine drops below the desired speed, governor weights l7 and II will move inwardly in the direction indicated by the dotted arrows thereby permitting yoke 21 to move downwardly, thus increasing the supply of fuel to the controlled engine. In this manner the speed of the controlled engine is always returned to the preselected desired value.

In order to reduce the rate at which piston 66 can move vertically within chamber 62, the dash pot arrangement shown most clearly in Figs. 1, 4 and 5 is provided. As previously pointed out, chamber 63 of housing 60 is filled with a hydraulic fluid. Thus when piston 66 is moved upwardly within chamber 62, any hydraulic fluid trapped above piston 68 must flow through channel 39 to the underside of said piston. The rate of flow through channel 89 is controlled by means of stem 92 in the manner hereinbefore indicated. If, on the other hand, piston 66 is moved downwardly within chamber 62, any hydraulic fluid trapped below piston 68 must flow through channel 89 into the space above piston 68. In this manner the movement of piston 60 within chamdrical walls *thereof.

ber152 istdaniped 1811111113318 tendency of the governow it!) ihun't -is rneduced.

simplified lair vpiston :arrangement :is shown in "1, this arrangement performing .the same function thatshown in Eigs. i=1 tofi. Referring torFig. H, M :designates azsleeve into which r plug member 46 defining ;conically-=shaped tip 41 is sorew-threadedly engaged. Bracket 5 I supports cylinder housing :member 55 above cap member 4910f governor :housing '-.I 0. Cylinder housing -55 defines an upper chamber :I 50 and lower chamber I51,"said chambersheing nseparated :.by means of "a partition I452. .A central opening 153 extendsrthroughssaid partition. A piston IMnarrying a :sealing :mem'ber I55 on its .outer periphery is :slidably iarranged within chamber I-5-I in sealing icontaot with =the cylindrical walls thereof. A ipiston A56 marrying .a :sealing member I51 on its ".outer periphery :is :slidably disposed with-in chamber 150 msealing teontact with the cylin- A-connecting trod I58 extending through opening I53 mechanically conneotspistons I56 and I 54. A .sealing ring -I5s is zprovided around {connecting rod 158 to form afluid-tightsseal between said :rod and partition I52. A passage I50 extends from the upperiace I fil :of piston A56 5130 the :lower face I52 of said piston. ri ohannel I3;extends through partition I52 \the upper face 154 .of chamber I I, screw threads 1| 65 .-being provided at the-1outer terminus of wharmel 416.3 for iconnection to the source of air under pressure. Threaded .bore I56 extends through the upper wall I161 ofcylinder housing 61] rand'iseadapted .to .receive a threaded plug I68 tor'closing said bore. Chamber I50 isfilled with a rhydraulic .fluid, preferably oil.

Air under (the desired [pressure is admitted to chamber rI 5I-.thnou gh channel I.63. .This air :tends to .force piston -.-I 54 downwardly within chamber L51. Since .piston .I 54 .is mechanically :connected to piston 4:56 .by connecting rod I58, piston I55 also tends to move downwardly. :If pistons I54 and -I5 6 -:.are not-in their full .down position (that is, .aszshown injig. 7) then thehydraulic fluid trapped between the .lower .face of piston 156 and ;partition 4.52 .is .forced to now through passage 4161], .thus .retarding the -.speed of movement dr pistonsl-I 5 l andISB. Whenpiston I54 ismoved upwardly by .the upward .force exerted through plug J6, ypiston Il55is also moved upwardly. .In

this case, rtheihydraulic fluid above piston I56 must flow through passage 150 .of .the lower .face of .said ;piston. Again, .the rate at which pistons I5! .and 'II'SB can move is retarded :by the .flow of Ihydraulic fluid through passage 160. -It will be understood, or course, that .the diameter of passage "I50 and the viscosity of .the hydraulic fluid employed determine the amount of resistance "'ofiered to "the vertical movement of the pistons.

*Tnstead =0: employing air actuated 'piston 65 in *theembo'diment illustrated "in-Figs. l to "6, in- (Elusive, any air actuated mechanism which is capable (if moving longitudinally-under opposing the upw'ard movement of stem 33 may be 'employed. For example, an *air actuated resilient diaphragmimay be employed. Such an air" actuated :mechanism is illustrated in Fig. -8, this mechanismzrepla'cing ithe air actuated piston arrangement:showninrEig.1. .Referringto Fig. 8, numeral 44 iclesignates the sleeve member projecting -through 'the atop of the governor-housing and carrying plug d5 provided with ;a iconicalshaped tip 41. .supportedby .members :51 15 air diaphragm housing I70. Housing Iii) defines -.a

chamber Hal, said .chamher being sed by means of a resilient diaphragm 4112 which may be secured ,to said housing by *means 10 ring M3 secured to housing are by means of a plurality of bolts 1:14,. .A ifitting M6 is ovided 23.1; the upper end of chamber :IFM .ior admission of air under pressure irem a source, not -shown,- to said chamber. Resilient-diaphragm A32 may :be madeof any material which impervious torair and which is :capable of repeated flexure and may suitably :be :made of either natural or synthetic rubber.

Housing iii ii also defines zoylindrical chamber 354 in which isanountedipiston .-I 18 carryingsealing means i it :on its outer ;per,i =ph6ry..said piston is :longitudinaily .rnevable .in -.s,ai;d chamber sin datight relation with (the Walls zthereof. his-ton i is provided with channel 495 which extend rthreughrsaid piston from the .upper surface ,to the Jower surface thereof. .Partition :I 85 separates diaphragm chamber 1-1?! and piston chamber I is? -.an d-:.defines anwopening t8! :extending therethrough. .Rod M2 is .=mechani cal1y affi-xed at one :end :to diaphragm 1112 and mechanically afii-xed at the other =.end to. piston M8,. Seal-mg means s33 :15 disposed in 11a recess surrounding ropening I 8:! for providin -:a .fiuid-tight seal around grad 1 13.2 as rit moi/es "thro h said partition. Mechanicallyiaffixedtorthe upper-side of piston 1.718 is :rod :Iill avhich {extends through opening H35 inhousing 1 KB. vSealing means .185 is disposed in .a sreeess in housing Ml? surrounding opening {85 .for providing a :fiuidstight :seal around rod 118 2 as itmoves rthroughasaidtonening. The upper 1511,51 it?! of rod .1185 :is Provided with screwthreads. honin -retaining member A83 is sererwthreadediy en aged with :the threaded upper end as": of and use :andaiam :nut @139- is als threadedly en aged with :said and ifer abutment on .spring-retaining member 438.. Aj-Sprlng its!) is concentrically arranged around :rod I84, its upper end Ia! {abutting -.on ispning-rretainin member A288 :and its flower rend i912 abutting :on housing :I "in to ;biasrspringnetaining.member r4818 away .trom housing till. Housing :IFHJ :ispmuided with :fillermole A153 which riscclosable :by means of screwthreaded z-plng flh ber E :1 filled with :a rhydraulic fluidesuchias .oil.

-;It will be :understood that instead sOf providing channel :I $15 in piston xl'simior permitting Etheaflow of hydraulic fluid therethrough 1as :piston :t-IB -:is moved longitudinally within chamber 11-5151,, the adjustable rorifice arrangement :shown in :E'igs. 4 and 5 :may :be .used rand igreater :eontrol secured thereby.

:Since :the ';only essential rdifierence rbetween :the showing of 8 and the :showingrof iEig. 1 is the :substitution ref -:rubber diaphragm 1:12 for piston 'fifi rand sinoe zthe operation of the embodiment shown insliligsS sisiniprinciplathessameias the i operation of zthe rembodiment showniinFig. :1, the operation rof stile-embodiment of .?Eig.l8-Wi11 not z-be Jfurther :described.

:It will :be apparent that various rchanges be made ithe idevice .cillustrated a-and zdeseribed without {departing from :theispirit :of the present invention. .It @will the further obvious Ethat :the objects hereiribeiore mentioned, :as -.well=as other objects, 1 are :"attained by :the device :of =theipresent invention.

Having :fullycillustrated :and :described the {device of the present :invention, what I :wish :to claimzand secure by Letters Patent :is:

:1. spring-:loaded zgovernor ifOI' .zmaintaining the :speed -:of iarotative :prime mover within treasonably constant limits and adjustable for different speeds comprising a spindle for rotation about its longitudinal axis; a pair of weights pivotally mounted on said spindle for arcuate movement when said spindle is rotated; a plurality of springs mounted in tandem and arranged to oppose successively the arcuate movements of said weights as the rotative speed of said spindle is increased and an air actuated mechanism including a dash pot arranged to augment the force exerted by said plurality of springs.

2. A spring-loaded governor for maintaining the speed of a rotative prime mover within reasonably constant limits and adjustable for diiferent speeds comprising a spindle adapted for rotation about its longitudinal axis by said prime mover; a pair of weights pivotally mounted on said spindle for arcuate movement on rotation of said spindle, said weights being arranged to move outwardly from the longitudinal axis of said spindle as the rate of rotation of said spindle is increased; a first spring of low spring rate and a second spring of high spring rate mounted concentrically of said spindle, said springs being arranged to oppose successively the outward arcuate movement of said weights; and an air actuated mechanism including a dash pot arranged to augment the force exerted by said first and said second springs in opposing the arcuate movement of said weights.

3. A spring-loaded governor for maintaining the speed of a rotative prime mover within reasonably constant limits and adjustable for different speeds comprising, in combination, a governor housing; a spindle mounted in said housing for rotation about its longitudinal axis; a pair of weights pivotally mounted on said spindle for arcuate movement on rotation of said spindle, said weights being arranged to move outwardly from the longitudinal axis of said spindle as the rate of rotation of said spindle is increased and to move toward the longitudinal axis of said spindle as the rate of rotation of said spindle is decreased; a yoke mounted in said governor housing for longitudinal movement with respect to said spindle on arcuate movement of said weights; a first spring of low spring rate biasing said yoke in a direction to oppose the outward movement of said weights;

a governor stem yieldably supported by said yoke and longitudinally movable by said yoke as said weights move outwardly; a variable pressure air-loaded mechanism including a dash pot disposed in the path of said governor stem for yieldably opposing longitudinal movement of said stem as said weights move outwardly; and a second spring of higher spring rate than said first spring disposed about said governor stem to oppose the longitudinal movement of said yoke when longitudinal movement of said stem is opposed by said air-loaded mechanism.

4. A spring-loaded governor for maintaining the speed of a rotative prime mover within reasonably constant limitsand adjustable for different speeds comprising a governor housing; a spindle mounted in said housing for rotation about its longitudinal axis; a pair of weights pivotally mounted on said spindle for arcuate movement on rotation of said spindle, said weights being arranged to move outwardly from the longitudinal axis of said spindle as the rate of rotation of said spindle is increased and to move toward the longitudinal axis of said spindle as the rate of rotation of said spindle is decreased; a yoke mounted in said governor housing for longitudinal movement with respect.

to said spindle on arcuate movement of said weights; a first spring of low spring rate biasing.

said yoke away from an end of said governor housing and opposing the outward arcuate movement of said weights; a governor stem carrying a first spring-retaining member slidably mounted on one end thereof for limited longitudinal movement with respect thereto .and carrying a second spring-retaining member afiixed thereto adjacent the other end thereof, said first spring-retaining member abutting on said yoke and the other end of said stem extending through said end of the governor housing and freely movable therethrough; a second spring of higher spring rate than said first spring biasing said first spring-retaining member away from said second spring-retaining member; and an air actuated mechanism including a dash pot mounted on said end of the governor housing and disposed in the path of said governor stem, said means being arranged to be acted upon by air to oppose the movement of said stem caused by the outward arcuate movement of said weights.

5. A spring-loaded governor for maintaining the speed of a rotative prime mover within reasonably constant limits and adjustable for different speeds comprising, in combination, a governor housing; a spindle mounted in said housing for rotation about its longitudinal axis; a pair of weights pivotally mounted on said spindle for arcuate movement on rotation of said spindle, said weights being arranged to move outwardly from the longitudinal axis of said spindle as the rate of rotation of said spindle is increased and to move toward the longitudinal axis of said spindle as the rate of rotation of said spindle is decreased; a yoke mounted on said governor housing for longitudinal movement with respect to said spindle on arcuate movement of said Weights; a first spring of low spring rate biasing said yoke away from an end of said governor housing and opposing the outward arcuate movement of said weights; a governor stem carrying a first spring-retaining member slidably mounted on one end thereof for limited longitudinal movement with respect thereto and carrying a second spring-retaining member aflixed thereto adjacent the other end thereof, said first spring-retaining member abutting on said yoke and the other end of said stem extending through said end of the governor housing and freely movable therethrough; a second spring of higher spring rate than said first spring biasing said first spring-retaining member away from said second spring-retaining member; va cylinder housing defining a first cylindrical chamber fluidly connected to a source of air under pressure mounted on said end of the governor housing; a piston slidably arranged in said first chamber in fluid-tight relation with the walls thereof and disposed in the path of said stem, said piston beingarranged to be acted upon by air to oppose the movement of said stem caused by the outward arcuate movement of said weights and a dash pot mechanically connected to said piston.

6. A device in accordance with claim '5 in which a third spring of lower spring rate than said first spring is arranged to bias said piston in a direction opposite to the direction which said piston is caused to move by reason of said air pressure.

7. A device in accordance with claim in which said dash pot is formed by the cylinder housing defining a second cylindrical chamber with a piston having a channel extending therethrough disposed in said chamber in fluid-tight relation with the walls thereof, said second cylindrical chamber being filled with hydraulic fluid.

8. A spring loaded overnor for maintaining the speed of a rotative prime mover within reasonably constant limits and adjustable for difierent speeds comprising, in combination, a governor housing, a spindle mounted in said housing for rotation about its longitudinal axis, a @pair of weights pivotally mounted on said spindle for arcuate movement on rotation of said spindle, said weights being arranged to move outwardly from the longitudinal axis of said spindle as the rate of rotation of said spindle is increased and to move toward the longitudinal axis of said spindle as the rate of rotation of said spindle is decreased, a yoke mounted on said governor housing arranged to be moved along the axis of said spindle upon arcuate movement of said pair of weights, a mechanical linkage for connectingsaid yoke with the fuel rack of said prime mover,

9. A device in accordance with claim 8 in which said spring loaded means interconnecting said yoke with said piston includes a lost motion connection.

10. A device in accordance with claim 8 in which said spring loaded means is a spring loaded telescoping assembly interconnectin with a lost motion connection said yoke with said piston.

11. A device in accordance with claim 8 in which said spring loaded means is a telescoping assembly spring loaded with an over-speed spring and interconnecting with a lost motion connection said yoke with said piston.

ROBERT R. CROOKSTON.

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